Planetary piston displacement mechanism



3 Sheets-Sheet 2 H TTOENE Y July 19 1949- J. o. PoRTEOus 2,476,383

PLANETAHY PISTON DISPLACEMENT MECHANISM Filed Dec. 22H, 1945 lC. Sheets-Sheet 3 IN VEN TOR.

JOHN O. Poem-005 BY 6o 63 l 6, ma@ um /ITTORNEY Patented July 19, 1949 UNITED STATES TENT OFFICE PLANETARY PISTON DISPLACEMENT MECHANISM John 0. Porteous, Pasadena, Calif.

Application December' 22, 1945, Serial No. 636,747

7 Claims.

This invention relates generally to fluid displacement mechanisms, and more particularly to pumps, compressors and similar devices.

An object of the invention is to provide a device for developing fluid pressure in fluid circulating and static systems, which is characterized by high volumetric eliciency; simplicity of construction with a minimum number of parts; dependable operation with negligible maintenance over extended periods of time; automatic pressure lubrication of its working parts to reduce wear to a minimum; and freedom from leakage of lubricant and the uid being pumped.

Another object of this invention is to provide a huid displacement device of the above described character whose fluid-tight seal for the operating or drive shaft of the device is arranged at the low pressure side thereof so as to obviate the present common failure of this type of shaft seal which is required to be installed at the high pressure side of various devices heretofore proposed.

A further object of the invention is to provide a fluid displacement device in which any iiuid and lubricant which may reach the shaft seal, will be collected to effect its return to the lubricant reservoir of theI device.

Still another object of the invention is to provide a iiuid displacement device, which, in its more specific aspect, includes a piston having a peripheral working surface and being mounted on a cam of the operating shaft, with the axis of the piston eccentrically related to the axis of such shaft and with the piston compelled to oscillate through a predetermined angle about an axis eccentrically related to the shaft axis, as the piston is driven by the cam, to the end of effectively dampening mechanical vibration resulting from the eccentrically mounted'unbalanced piston, and with the piston operatively related to an induction port to control same in a manner to admit uid to a working chamber between vanes riding on the periphery of the piston, for pumping of fluid from the low pressure side of the device through the working chamber.

A still further object of the invention is to provide a uid displacement device whose working parts as above described are exposed to the cooling effect of gas entering thev low pressure chamber of the device, whereby to obviate any `and all extraneous cooling m'eansfor the working parts and yet insure a cool running condition of the device irrespective of continuous and sustained operation. f

With these and other objects Am view, the in- 2 vention resides in the combinations, arrangements and functional relationships ofelements as set forth in the following specification and particularly pointed out in the appended claims.

l'n. the accompanying drawings,

Figure l is a longitudinal axial sectional view of one form of uid displacement device embodying this invention;

Figure 2 is a transverse sectional view taken on the line 2-2 of Figure l;

Figures 3 and 4 are views similar to Figure 2 and illustrating positions of the piston progressively advanced from that shown in VFigure 2;

Figure 5 is a reduced scale view of the fluid displacement device in front elevation with a portion of the housing in section to expose interior mechanism;

Figure 6 is a fra-gmentary detail sectional view taken on the line 6 6 of Figure 4; and

Figure '7 is a diagrammatic view illustrating movements of the piston.

Referring specifically to the drawings, the invention in its present embodim'ent comprises a housing I-I composed of a support I0 anda cover E'I, the support being in the form of a disk, and the cover being a cup having a flange Ila. receiving bolts I2 which pass through the support to rigidly secure the latter and cover together for co-action in defining alow pressure chamber i3 having an inlet I4 for fluid to be circulated by the device.

The support lil is provided eccentrically thereof with a hub I5 supporting a bearing I6 in which is .rotatably mounted one journal II of an operating or drive shaft I8 whose other journal I9 is rotatably mounted in a second bearing 2i! supported in the hub 2|I of a bearing member 22. Cap screws 23 pass through the bearing member 22 and through a stator member 24, and are threaded into the support I0 to rigidly secure such members to the support with the bearing member spaced from the support by the stator member, and the confronting flat surface Z5 and 26 (Figure l) of the respective members in parallelism and perpendicular to the axis of the shaft I8.

Fixed to or formed integral with the shaft I3 between its journals Il and I9 is a cam 3il in the form of an eccentric disk whose axis is eccentrically related to the shaft axis, and whose width or face is such as to provide a working nt between the surfaces 25 and` 26. A piston 3i in the form of a disk having a peripheral working surface 32 is also provided with a central bore 33 receiving the cam so as to mount the piston thereon for movement eccentrically by the cam in a circular path about the axis of the shaft I8 as a center.

The stator member 24 is generally segmental, and more specifically semi-circular in plan to provide an internal annular working surface 35 whose center is coincident with the axis oi the shaft I8. Varies 35 and 31 are mounted in radial slots 38 and 3.9 respectively, in the stator member 24, and are urged by coil springs 45 and il into wiping engagement with the peripheral working surface 32 of the piston 3|. The springs lil and lil are interposed between the vanes and removable plugs 42 and 43 screwed into the stator member 24 and provided with breather passages 44 and 45 which prevent air pressure from being built up behind the vanes as the latter work in the slots 38 and 39.

The piston 3| and vanes 35 and 31 are of such width as to have a working fit between the surfaces 25 and 2B, and co-act with the support lil, bearing member 22 and stator member 2d to de fine a working 'chamber 50 having an inlet 5i and an outlet 52. The inlet is in the form ci a piston-controlled port (Figures 1 and 5) in the bearing member 22, communicating with a duct 5 Ia in the member, to which is connected one end of an induction pipe 5lb, the other end of which is co-axially related to and slightly spaced from the inlet I4 of the low pressure chamber i3, all to the end of protecting the port 5I against the entry of lubricant from the chamber I3 with the fluid being pumped.

The outlet 52 is located in the stator member 24 adjacent the vane 31 and is controlled by an 1 outwardly opening check valve 53 normally urged to close the outlet by a spring 54 arranged in a chamber 55 and bearing against the valve and against a removable plug 58 screwed into the chamber. From the chamber 55 lead registering passages 51 and 5B (Figure 1) in the stator mem- -ber 24 and support I0, respectively, through which fluid is forced from the working chamber 5i! into a pipe 59 which can form part of a fluid circulating or delivery system.

The piston 3| is provided with a radial slot 55 slidably receiving a guide member 6| in the form of a rectangular metal block having a bore 52 receiving the shank of4 a pin 53 reduced and threaded at one end 64 and provided with a head 55 at its other end. The pin is rigidly screwed into a bore 66 in the support Iii and mounts the guide member 5| for pivotal movement about an axis parallel to and eccentrically ci the axis of the shaft I8 so as to control movement of the piston 3l on the cam in a manner to be later described.

In practice, the low pressure chamber i3 i supplied with lubricant whose level is approximately indicated in Figure 4 so that the lower portion of the piston is immersed in the liquid. Lubricant from this supply is automatically de livered to working parts and surfaces of the device, and to this end the portion of the slot 58 between its closed inner end and the guide member 5I constitutes a pump chamber having an inlet port controlled by the guide member, and an outlet port 'Il adapted to register at a predetermined position of the cam 33 in the cycle of operation, with a radial passage 172 in the cam, communicating With an axial passage in the shaft I8. Lateral passages 'I4 and 15 in the shaft I8 lead from the axial passage 13 to circumferential channels 13 and'19 in the bearings i5 and Cil `4 28, for the distribution of lubricant to all working parts.

The guide member 6I functions as a piston so as to provide a pump operable to draw lubricant from the low pressure chamber I3 through the inlet port 18 into the slot B8 when the port is momentarily uncovered by the guide member, following which the guide member closes the inlet port and forces the charge of lubricant from the slot 68 through its outlet port 'II into the radial passage 12 which registers with such out-- let port at the proper time, and whose communication with the outlet port is prolonged by a circumferential extension of the passage ifi as shown in Figure 3.

The outer end of the shaft I8 passes through a shaft seal (Figure 1) comprising a chamber 323 surrounding the shaft I8 in the outer end portion of the hub I5 and freely receiving an elastic sealing member 9| mounted on the shaft in a metal cup 92 and urged by a coil spring 93 in one direction to maintain an annular 'bearing surface 94 on the cup in engagement with an annular bearing surface 95 in a gland nut 96 threaded at 91 on the hub I5 and freely receiving the shaft. The spring 93 is interposed betweenthrust washers 98 and 99, one of which seats against a shoulder |80 on the shaft I8, and the other of which seats against the sealing vmember 9| to press the latter into sealing engagement with the shaft. Any lubricant which reaches the chamber 95 is prevented from accumulating therein by the provision of a passage YIEII Vwhich places the -chamber 98 in communication with the low pressure chamber I3 for the return of accumulated lubricant thereto, thus augmenting the action of the seal in preventing leakage of lubricant from the housing I-I around the shaft I8.

The operation of the invention is as follows:

Let it be assumed that the inlet I4 and the outlet pipe 59 are respectively connected to the low and high pressure sides of a refrigerator system for the compressing and circulation of a refrigerant therein by the device. With the working parts of the device in the positions shown in Figure 2, and with the shaft I8 being driven in the counterclockwise direction of the arrow by an electric motor or other 'prime mover (not shown) ,movement of the piston3l from the position shown in Figure 2-to the position shown in 'Figure 3 wherein the working chamber has reached its maximum capacity, has created a partial vacuuin inv the working chamber so that the piston uncovers the port 5I as shown in Fig ures 1 and 5, duid fromA the low pressure chamber I3 will be admitted directly from the inlet Iii to the working chamber s0 as to protect the port 5I against the entrance of lubricant with the fluid being pumped.

As movement of the pistonI from its position of Figure 3 continues, the Charge of fluid in the working chamber 59 will be compressed by the piston as shown lin Figure 4, so as to be forced through the outlet 52 past `the valve 53, thus completing the cycle of operation which taires place during each revolution of the shaft I8.

VIt `will be clear that the vmotion imparted to the piston 3| by the combined actions of the cam 30 'and guide member 6I causes a point on the pe ripheral surface of the piston to' travel in the generally oval path B as shown in Figure 7, so that the period-of vibration-of' the eccentrically mounted piston willbe broken up and thus materially dampened so as to contribute to a Smooth running mechanism.

It will be noted that the shaft seal is subjected only to low pressure due to the fact that the lov.7 pressure chamber I3 is in communication with the suction side of the unit. The only path of leakage for high pressure iiuid from the working chamber 5i) is between the walls 25, Z past vanes 36 and 3l. Any pressure which might escape from the working chamber 50 returns to the suction side of the unit into the low pressure chamber It and is repumped, so that a low pressure condition is maintained in the chamber I3 at all times during operation of the pump. Thus, the fluid sealing efficiency of the shaft seal is maintained at a maximum, and premature failure of the shaft seal as installed at the high pressure side of pumps heretofore proposed, is avoided.

Furthermore, it will be noted that as the working parts of the machine are all located in the low pressure chamber I3, they are exposed to the cooling effect of the fluid returning to the lor.' pressure chamber through the inlet It, thus eliminating the need for a cooling system for these parts, and protecting the parts against overheating irrespective of sustained and continuous operation of the machine.

I claim:

1. In mechanism of the class described, a housing defining a low pressure chamber having iiuid inlet; a shaft journaled in the housing; a fluid-tight seal through which said shaft projects into the chamber so as to subject said seal only to the low pressure which exists in said chamber; a piston in said chamber operatively connected to the shaft for actuation thereby; means co-acting with only a portion of the piston to define a segmental working chamber having an outlet for compressed fluid, with the remaining portion of the piston within the low pressure chamber; and means operable in response to actuation of the piston to cause the latter to pump fluid from the low pressure chamber through the working chamber;

2. In mechanism of the class described, a housing defining a low pressure chamber having an inlet; one Wall of said housing having a bearing; a bearing member in said chamber; a segmental stator member spacing said bearing member from said wall; a shaft journaled in said bearing and bearing member; a cam on said shaft having an axis eccentrically related to the shaft axis; apiston having a peripheral working surface and mounted on said cam between said wall of the housing and the bearing member for co-action therewith and with the stator member in defining a segmental working chamber; means co-a-cting with the piston to prevent its rotation about its axis and compelling oscillatory movement of the piston about a second axis diametrically opposite to said working chamber and offset from the shaft axis, when the piston is driven by the cam; and means co-acting with the piston by which the latter effects pumping of fluid from the low pressure chamber through the working chamber.

3. In mechanism of the class described, a housing defining a low pressure chamber having an inlet; one wall of said housing having a bearing; a bearing member in said chamber; a segmental stator member spacing said bearing member from said wall; a shaft journaled in said bearing and bearing member; a cam on said shaft having an axis eccentrically related to the shaft axis; a piston having a peripheral working surface and mounted on said cam between said wall of the housing and the bearing member for co-action therewith and with the stator member in dening a segmental working chamber; means co-acting with the piston to prevent its rotation about its axis and compelling oscillatory movement of the piston about a second axis offset from the shaft axis, when the piston is being driven by the cam; varies slidably mounted in the stator member and urged into engagement with the peripheral surface of the piston, to define the ends of said working chamber, and beyond which vanes the piston is exposed in the low pressure chamber for the free circulation of low pressure iuid therein around the piston; the bearing member having a port communicating with the low pressure and working chambers and controlled by the piston to admit fluid from the low pressure chamber to the working chamber for compressing by the piston; and a valve-controlled outlet for the working chamber through which compressed fluid is forced by the piston.

4. In mechanism of the class described, a housing dening a low pressure chamber having a uid inlet; a shaft journaled in the housing and having a cam in said chamber; a piston having a peripheral working surface and mounted on said 'cam for movement of the piston in a circular path eccentrically of the shaft axis; the piston having a slot; a guide member mounted for pivotal movement about an axis oifset from the shaft and working in said slot for oo-action ther with in preventing rotation of the piston about its axis While rendering the piston free to move towards and away from said second axis; means co-acting with the piston to denne a segmental working chamber in which suction and pressure are alternately induced during movement of the piston while leaving the major portion of said piston disposed in the low pressure chamber for the iiow of the low pressure fluid therein around such portion of the piston; and means whereby fluid will be pumped from the low pressure chamber' through the working chamber by the piston during its movement.

5. In mechanism of the class described, a housing defining a low pressure chamber having a uid inlet; a shaft journaled in the housing and having a cam in said chamber; a piston having a peripheral working surface and mounted on said cam for movement of the piston in a circular path eccentrically of the shaft axis; the piston having a slot; a guide member mounted for pivotal movement about an axis offset from the shaft axis and working in said slot for co-action therewith in preventing rotation of the piston about its axis while rendering the piston free to move towards and away from the second said axis; means defining a segmental working chamber and including angularly spaced vanes urged into engagement with the periphery of the piston, with the portion of the piston beyond the ends -of the working chamber being disposed in said low pressure chamber; means defining a port controlled by the piston to admit fluid from the low pressure chamber to the working chamber for compressing by the piston; and a valve-controlled -outlet through which compressed fluid is forced from the working chamber by the piston.

6. In mechanism of the class described, a housing dei-ming a low pressure chamber having a 'uid inlet; a shaft journaled in the housing and lhaving a cam in said chamber; a piston having `a peripheral working surface and mounted on said cam for movement of the piston in a circular path eccentrically of the shaft axis; the piston having va slot; a guide member mounted for pivotal movement about a fixed axis offset from the shaft axis andworking in said slot for co-action there with in preventingrotation of the piston about its axis while rendering the piston free to move t0- wards and away from the second said axis; means dening a working chamber `of segmental form in which a corresponding portion of the piston .operates during its aforesaid movements to pump fluid from the low pressure chamber through the working chamber, while leaving the remaining portion of the piston clear ofthe Working chamber and exposed to the low pressure insaid low pressure chamber; said piston having a lubricant inlet disposed to be submerged in lubricant in the low pressure chamber, and placing-.the latter in communication with said piston slot under .the control of said guide member; the piston beius provided with a lubricant outlet-from said slot; said shaft having a lubricant passage adapt?- ed to placesaid outlet in communication with the journal surfaces of said shaft for the delivery of lubricant thereto in response to a pumping .ac-

tion created by said guide member` in said `Slot.

7. In mechanism of the class described, a support having` a bearing; a cover co-acting with the Supportto define a low pressure chamber having y a fluid inlet; a bearing member; a stator mem .ber ;y means securingsaid members to the support with the stator member spacing thebearing member from the support; a'shaft journaled in the bearings ofthe support and bearing member; a

cam `on the shaft spanning the space between the support and bearing member; a piston hav,-

ing a peripheral working surface and mounted ,on

said cam; vanes slidably mountedl in .said stator ,memberand normally urged into engagement 3 with the periphery of the pistonfor csi-action with the latter, they support, and said membersfin defining a Working chamber having an arcuate Working surface of segmental form leaving the major portion of the piston clear of the working chamber and exposed to the low pressure in said 10W pressure chamber; the piston having a slot; a guide member pivotally mounted on the support and operating in said slot to prevent rotation of the piston about its axis as the piston is driven by the cam; .means dening a port through which fluid from the low pressure chamber is admitted to said working chamber for compressing by the piston; and means dening an ,outlet .through which iiuid compressed -by the piston is forced from said working chamber.

JOHN O. PORTEOUS REFERENCES CITED The following references are of recordin the le of this patent:

UNITED STATES PATENTS 

